Profile milling machine



April 22, 1941- E. G.l RoEHM Erm. 2,239,625

v PROFILE MILLING. IACHINB Filed Feb. 13, 1939 6 Sheets-Sheet l A l A im] f" INKL... l gli, )s

April 22, 1941- E. G. Rot-:HM Erm. '2,239,625

PROFILE NLLING MACHINE" Filed Feb. 13, 1939 6 Sheets-Sheet 2 April 22, 1941. v E, Q RQEHM El-AL 2,239,625

PnoFILE uILLINe uAcHINE Filed Feb. 1s., 1939 e sheets-sheet s Ida? v INVENTOR. @AJ/#6 fof/w ATTORNEY.

April 22, 1941.

E. G. ROEHM EI'AL PROILE MILLING MACHINE Filed Feb. 13, 1939 e sheets-sheet 4 ATTORNEY.

'April 22, 1941. E G, RQEHN; UAL 2,239,625

PROFILE MILLING AGI-[INE Filed Feb. 13, 1939 6 Sheets-Sheet 5 INVENTOR.

mov/L ATTORNEY.

April 22,1941. E. G. RQEHM. mL- 2,239,625

PROFILE MILLING uAcHINE Filed Feb. 13, 1939 6 Sheets-Shea# 6 INVENTOR.

z//fy G @ff/N ATTORNEY.

Patented Apr. 22, 1941 UNI izo STATES PATENT OFFICEA morire MILLING MACHINE Erwin G. Roehm, Norwood, and Hans Fritschi, Silverton, Ohio,v assgnors to The Cincinnati Milling Machine Co., Cincinnati, Ohio, a corporation oi' Ohio Application February 13, 1939, Serial No. 256,080

an improved manually guided tracer controlled milling' machine.

A further object of this invention is to provide improved means for tracer controlling the movements of a cutting tool.

An additional object of this invention is to provide a dual purpose machine of the character described with improved control means for each purpose, together with interlocks and safety features whereby controls not necessary to the selected method-of operation can not be inadvertently actuated, thus rendering the `machine safe in the hands of a comparatively inexperienced operator.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there'shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like refcrence numerals indicate like or similar parts:

Figure 1 is a front elevation of avmachine embodying the principles of this invention.

Figure 2 is a side elevation of the machiner Figure 7 is a perspective view of the control mechanism for the power transmission.

Figure 8 is a detail section on the line 8 8 of Figure 6.

Figure 9 is a diagrammaticV view of the hydraulic control circuit.

The general construction of the machine is shown in Figures 1 and 2 0f the drawings in which thereference numeral I0 indicates, in general, the bed of the machine upon which is formed a rst pair of guideways I l for receiving the table I2, and a second pair of guideways I3 for receiving the cross slide I4, it being noted that the cross slide moves in a direction normal to the axis of movement of the table.

The cross slide, I4 has a pair ofguideways I5 upon which is mounted va vertically slidable tool head I6 so that the axis of the milling tool, such as I1, is perpendicular to the plane of movement 'is adapted to be driven by a prime mover, such as the electric motor I9, shown in Figure', 2,

through a. suitable known transmission. This transmission may be of any known type, and

Asince it does not constitute any part of this invention, the details thereof are not illustrated. This' .machine is a dual purpose machine, the

'first of which is to mill plane surfaces, and the second of which is to mill irregular surfaces, known in the art as profiled surfaces.

Plane surfaces may be produced in various ways, such as traversing the table while the cross slide remains stationary; locking the table and moving the cross slide; or simultaneously moving both slides whereby the path of cutting will be at an angle to the direction of movement of both slides. AThe vertical slide is utilized .more particularly for setting or determining the depth of cut, although with suitable tools, countersinking and boring operations may be performed.

Suitable controls, to be described hereafter, are provided for controlling the movementsv of the table and cross slideV during plane milling. When the machine is utilized asa profiling machine a different set of controls is provided whereby a single element, such as the tracer, may

simultaneously control either direction of movement of the two slides. Improved interlocking features are provided between the different sets of controls for guarding the opera-tion of the machine,

Regardless of the method of'control, or the purpose for which the machine is to be utilized, each slide actually moves in all cases by hy- ,draulic motors, which are illustrated as being of the piston and cylinder type.

Referring to Figure 9, the table l2 is actuated by the piston 20 contained in the cylinder 2l and connected to the table by a piston rod 22. The

cross slide I4 is actuated by a piston 23 contained in a cylinder 24 and connected to the crass slide by the piston rod 25. The vertical slide |6 is actuated by a piston 26 contained in a. cylinder 21, the cylinder being integral with the silde and the piston 26 being connected by the piston rod 28 to the cross slide |4. The admission of pressure to the cylinder 21 is controlled solely by a servo-control valve indicated generally by the reference numeral 29, which has a central pressure port 30, a pair of motor ports 3| and 32, and a pair' of exhaust ports 33 and 34. 'I'he motor ports 3| and 32 are connected by channels 35 and 36 to opposite ends of the cylinder 21. The valve has aplunger 31 upon which is formed a central spool 38 normally in a position to close the pressure port 30, and a pair of annular grooves 39 and 40 formed on opposite sides of the central spool for alternately connecting the pressure port to one of the motor ports, and simultaneously connecting the other motor port to an exhaust port for effecting movement of the slide.

A servo-control valve 4| is provided for controlling admission offluid pressure to the table cylinder 2| during plane milling operations, and for set-up purposes. 'Ihis valve has a pressure port 42, a pair of motor ports 43 and 44 and a pair of exhaust ports 45 and 46. The valve 'plunger 41 has a. central spool 48 for normally closing the pressure port, and a pair of annular grooves 49 and 50 on opposite sides of the spool for selectively connecting the pressure port to one of the motor ports, and simultaneously the other motor port to exhaust for causing actuation of the table.

The admission of fluid pressure to the cross slide cylinder 24 during plane milling opera- 35 tions and for set-up purposes is controlled by a servo-valve which has a pressure port 52, a pair of motor ports 53 and 54 and a pair of exhaust ports 55 and ,56. The valve plunger 51 has a central spool 58 for normally closing the pressure port, and a pair of annular grooves 59 and 60 on opposite sides of the spool for selectively connecting the pressure port to one of the motor ports and simultaneously the other motor Port to exhaust.

The cylinders 2| and 24 are connected to their respective -servo-control valves through a selector valve mechanism, indicated generally by the reference numeral 6|. This mechanism comprises two valve plungers 62 and 63 which are mechanically interconnected by a centrally pivoted lever 64, whereby upon rotation of the lever the valve plungers will be shifted in opposite di-l rections.

The lever 64 is keyed to a shaft 65 which has an operating handle 66 xed to the end thereof for manual actuation, the lever being shown in Figures 1 and 2 of the drawings. The selector valve mechanismis mounted in a housing 61 attached to the front of the machine.

'Ihe object of the selector valve mechanism is to condition the hydraulic circuit for either one of the two methods of operating the machine. In other words, in one position of the selector valve mechanism the two servo-control valves 4| and 5| are hydraulically connected to their respective cylinders 2| and 24. f

In the other position of the selector valve mechanism, the servo-valves are hydraulically disconnected from the respective c;linders 2| and 24, 70 and these cylinders are connected hydraulically to a tracer controlled valve. These various connections are established by the following means.

The valve plunger 62 is slidably mounted in a sleeve 68 which has a pair of ports 69 and 75 ally fixed sleeve 96.

10 to which are connected channels 1| and 12 leading to ports 13 and 14 located in opposite ends of the cylinder 2|. With the plunger 62 in the position shown in Figure 9, the ports 69 and 10 are connected by the annular grooves 15 and 16 to ports 11 and 18. These latter ports are connected by channels 19 and 80 to the motor ports 43 and 44 of the servo-valve 4|. The plunger 63 is slidably mounted in a sleeve 8| which has a pair of ports 82 and 83 connected by channels 84 and 85 to ports 86 and 81 located in opposite ends of the cross slide cylinder 24. With the plunger 63 in the position shown, the port 83 is connected by the annular groove 88 to port 81 and the port 82 is connected by the annular groove to port 9| .4 The ports 89 and 9| are connected by channels 92 and 93 t motor ports 54 and 53 respectively of the servo-control valve 5|. It will now be.apparent that shifting of either servo-valve will cause movement of the respective slide.

'Ihe servo-valves 4| and 5| are adapted to be shifted manually, or by power at a`plurality of feed rates or at a rapid traverse rate. Since duplicate control mechanisms are provided for each valve, only one mechanism will be described, it being understood that a duplicate A mechanism is provided for controlling the other servo-valve,

Furthermore, the construction of all three servo-valves is the same, and therefore, only one of these will be described, reference being had to Figure 6. Assuming the construction shown in Figure 6 as applied to the table, the servovalve will therefore be indicated by the reference numeral 4|. and the plunger by the reference numeral 41. The plunger 41 has clutch teeth 94 on one end which intermesh with clutch teeth formed on the end of a driving sleeve 96. The sleeve 96 isrotatably mounted in anti-friction bearings 91, which also hold it against axial movement with respect to the fixed housing 98. The object of the clutch teeth is to permit axial movement of the plunger 41 relative to the axi- A lead screw 99 passes through the plunger 41 and the sleeve 96 and is attached at opposite ends to the movable slide, which, in this case, is the table I2. 'I'he screw acts as a feed back connection from the movable slide to the servo-valve.

'Ihe valve plunger 41 has an enlarged head |03 formed on one end thereof in which is pivotally mounted, as shown in Figure 8, the half nut |0|. A spring |02 normally holds the half nut into engagement with the lead screw 99. An actuating gear |03 is formed integral with the sleeve 96 and it will now be apparent that 4upon rotation of this gear, and with the half nut in engagement with the lead screw 99, that the plunger 41 will be shifted axially relative to the sleeve 96 and thus establish a pressure connection of port 42 with the table cylinder 2|, and an exhaust connection from the other end of the cylinder whereby the piston 20 and connected slide will proceed to move. This movement will be fed ba( k to the lead screw 99, which will impart axial movement to the plunger 41 in a direction opiosite to that in which it was first moved, thus :ecentralizing the central spool 48 with respect to 'che port 42.

In the case of the vertical slide, the gear |03 will be a bevel gear so as to intermesh with a bevel gear not shown but attached to the end of the shaft |04 shown in Figure 1 and provided with a. hand wheel |05. It will thus 'be obvious hat upon rotation of the hand wheel |05, the rertical slide I6 may be adjusted relative to the `able.

The means for operating the gear |03 `as respects the table and cross slide consists .of the nanually rotatable handwheel |08, and a prime nover |01. The hand wheel |06 is mounted on ',he front of the machine as shown in Figure l ind is connected through 'a sprocket chain |08, iigure 6, and sprocket wheels |09 and ||0 to a haft The sprocket wheel is supported or free rotation on the shaft and it is necessary to connect the sprocket wheel to the shaft oy means of the shiftable clutch member ||2 in arder to impart rotation thereto. The shaft rias a gear ||3 keyed to the end thereof in mesh with the gear |03 for transmitting motion thereto.

For power actuation prime mover |01 is connected by a sprocket chain ||4 and sprocket wheels ||5 and ||6 to a shaft ||1 This shaft is continuously rotated during actuation of the prime mover and drives through gearing ||8 a friction disc ||9 which, in turn, rotates a friction disc |20.

The latter is splined on a shaft |2| and is shiftable relative thereto for moving the disc toward and from the center of rotation of the disc ||9 to thereby vary the rate of rotation of the shaft |2|. This constitutes a variable feed mechanism ofthe friction disc type. The shaft |2| drives a spiral gear |22 supported for free rotation on the shaft |23. The latter shaft has a spline portion |24 upon which slidesa rate determining clutch member |25 having an internal cone shaped face |26 for engagement with the cone |21 keyed to the end of the shaft ||1 for actuation of shaft |23 at a rapid traverse rate; and clutch teeth |28 on the other end for interengagement with similar shaped clutch teeth formed on the end of the gear |22 for actuation of the shaft |23 at variable feed rates The shaft |23 terminates in a bevel gear |29 which drives a pair of bevel gears |30 and |3| supported for free rotation on shaft in opposite directions. An intermediate clutch member |32 splined on the shaft serves to selectively connect the gears |30 and |3|-for actuation of the shaft in opposite directions. thus constituting a direction determinator or reverser. Thus, the shaft may be driven at one of several feed rates or at a rapid traverse rate, and in either direction, and lsince the clutch |32. has a neutral position, the entire power transmission may be disconnected from the shaft whereby the same may be rotated manually.

The positioning of the rate and direction determining clutches |25 and |32 is controlled by a single shaft |33 which, as shown in Figure 7, carries a cam |34 for operating the shifter |35 for the direction determining clutch |32; and a second cam |36 which is connected to the shifter |31 for controlling the position of the rate clutch |25. The shaft |33 has a detent plate |38 keyed thereto and this plate is connected by a link |39 to a crank arm |40 keyed to a vertical shaft |4|. The shaft |4| is mounted on thefront of the ing determined upon the direction of rotation of the plate |38 from its central position.

The parts may also be rotated in either4 direction beyond the feed position into -a rapid traverse position but' the parts must be held in the rapid traverse positionby the operator and as soon as he releases the handle |42 the spring pressed detent |46 will move theY plate back into the nearest feed position.

The cam groove |41 which controls the feedrapid traverse clutch |25 has a central arcuate portion ofthe same radius which holds the clutch |25 in a feed position during rotation of the plate through the angle measured between the notches |43 and |45. The cam groove |48 is shaped to produce an immediate shifting of the clutch |32 upon rotation of the cam in either I direction from a neutral position.

Y the clutch |32 willA be shifted into engagement with the gear |3|. Further rotation of the shaft in either direction beyond these positions will produce no further movement of the clutch. But further rotation of the cam |36 will bring into effect the opposite ends of the cam groove |41 which have a greater radius than the central portion of the cam groove whereby the clutch |25 will be shifted into a rapid traverse position. It will now be evident that the shaft |33 is capable of being moved into any one of five different positions to produce five different results.

It is desirable, when the power transmission is being utilized, to have the hand wheel |06 disconnected from the drive shaft and when the power transmission is not utilized, to have the hand wheel connected to the shaft. These different results are effected automatically by mechanism controlled from the shaft |33.` The clutch member ||2 is provided with a shifter fork |49 which is pivotally supported on the pin |50 and is continuously urged in a counterclockwise direction about this pivot by a hydraulic piston |5| to normally hold the clutch ||2 engaged. A spring |52 is connected to the end of the shifter to effect an urge thereon in a. clockwise direction whereby upon failure of the hydraulic pressure the clutch |I2 will be .disengaged, Vthereby preventing manual actuation of the servo-valve when no hydraulic pressure is present. In the neutral position lof the detent plate |38, a pin |53 carried by the shifter |49 engages a groove |54 in the plate, which groove is of suflicient depth to permit the clutch ||2 to be engaged.

Upon rotation of the plate |38 from itsneutral position, the pin |53 is causedA to ride out of the groove and cause disengagement of the clutch ||2. Therefore, this clutch is only engaged when the detent plate |38 is in a neutral position.

machine as respects the table and is provided; with'a manual control lever |42. The plate |38 has three notches |43, |44 and |45 formed in its periphery for receiving a spring pressed detent |46. When the detent, engages the central notch |44, the parts are in a neutral position, and when the detent engages either` the groove |43 or |45,

the parts are in a feed position, the direction be- The hydraulic system shown in Figure 9 is supplied with fluid pressure by a pump |55 which has an intake |56 through which fluid is withdrawn from a reservoir |51, and -a delivery line |58 which. is connected to Ia valve housing |59. The details of construction of this housing is shown in Figure 5. The reference numeral |60 indicates the port to which the delivery line |58 is `connected and this port communicates with a cross bore |6| which terminates at opposite ends in ports |62 and |63 to which are connected channels |64 and |65 for distribution of the fluid to different parts of the system. The bore |60 intersects an annular groove |66 formed in a xed sleeve |61. A plunger |68 is slidably mounted within the sleeve and is normally held in the position shown in Figure 5 by a spring |69.

The pump |55 may be designated as a feed pump for the reason that this pump supplies the fluid for operating the slides at feeding rates,

but when the transmission is adjusted to shift the servo-valves at a rapid traverse rate, the volumetric delivery of the pump |55 may not be adequate to supply the demand, and therefore, a second pump |10, which may be termed a rapid traverse pump, is provided for supplying additional fluid to the system during rapid traverse movement of either support. This pump has an intake |1|. through which fluid is withdrawn from the reservoir |51 and a delivery channel |12 which terminates in port |13 of the valve housing |59.

It will be noted from Figure 5 that the port |13 intersects a. second annular groove |14 formed in the sleeve |61. An annular groove formed in the plunger |68 normally interconnects the groove |14 with a groove |16 which communicates with the exhaust port |11. Thus, during normal operation of the machine, the rapid traverse pump. is connected through the valve housing |59 to reservoir. When the control mechanism shown in Figure 7 is adjusted to effect a rapid vtraverse movement, the plunger |68 is shifted.

against the compression of spring |69 by a hydraulically actuated piston |18 until the annular groove 15 interconnects the port |13 with the annular groove |66 and thereby the cross .bore |6|. In this way the delivery of the rapid traverse pump is added to the delivery of the feed pump.

The piston |18 is slidably mounted in a cylinder |19 and the end of cylinder is connected by a channel |80 to a pair of serially arranged valves |8| and |82, Figure 9. One of these valves is mounted in the feed box for the saddle and the other is mounted in the feed box for the table. The valve |82 may be assumed to be the valve shown in Figure 7. The plunger |83 of this valve has a follower |84 engaging a second cam groove |85 in the cam |34 attached to the shaft |33. This cam groove is annular throughout the extent of movement of the shaft |33 in either direction to effect feed rates but diverges beyond either feed position to cause shifting of the plunger |83 for either rapid traverse position of the shaft |33. Returning to Figure 9, the plunger |83 has an annular groove |86 which normally interconnects an exhaust port |81 to port |88, the latter being connected by channel |89 and valve |8| to cylinder |19. When the plunger |83 is shifted, however, a pressure port |90 is connected to the port |88 whereby fluid pressure is admitted to the cylinder |19 andthe piston |18 shifts the valve plunged |68 into a position to add the delivery of the rapid traverse pump to that of the feed pump. 'I'he channel |65 has a branch line |9| leading to the pressure port |92 of valve |8|, whereby this valve may also connect pressure to the cylinder |19 to cause connection of the rapid traverse pump to the system. The line |65 also has branch connections |94 and |93 which supply the pistons |5| that normally hold the manual control clutches I2 in an engaged position.

In order to perform profiling operations with this machine, a tracer mechanism indicated generally by the reference numeral |95 in Figure 3 is provided. This mechanism, although supported on the vertical slide for simultaneous movement with the cutter is provided with means for three directional adjustment with respect to the cutter vfor set-up purposes. In other words, the tracer mechanism is supported on guideways |96 formed on an L-shaped bracket |91, an adjusting screw |98 rotatably mounted in the bracket serves as means for manually positioning the tracer mechanism toward and from the cutter. The bracket |91 is slidably mounted in guideways formed on the saddle |99. An adjusting screw 200 is rotatably journaled on anti-friction bearings 20| in the bracket |91 and has a threaded connection with a nut 202 carried by the saddle |99. The screw 200 is connected by bevel gearing indicated generally by the reference numeral 203 to an operating shaft 204 which extends longitudinally of the bracket and is provided with a squared end 205 for application oi' a suitable wrench.

The saddle |99 is capable of cross adjustment by means of a screw 206 which hasa threaded connection with a nut 201 integral with the cross slide. The screw 208 is supported on vertical slide I6 and is provided with a squared end 208 as shown in Figure 1 for application of a suitable wrench.

By means of these three adjustments the tracer mechanism may be adjusted in any direction with respect to the cutter spindle to facilitate set-up or for removing the tracer mechanism to an inoperative position for straight milling operations.

I'he tracer mechanism comprises a tracer head 209 upon the top of which is mounted a valve block 2| 0. As shown in cross section in Figure 4 the valve block contains fourv valve sleeves 2| I, 2|2, 2|3 and 2|4 which are spaced 90 degrees apart. The valve .block is so positioned that the sleeves 2|| and 2|3 are parallel to the direction of movement of the table, and the sleeves 2|2 and 2|4 are parallel to the direction of movement of the cross slide. This makes the tracer 2| 5 which is pivotally supported at 2|6 in the tracer head and connected to the valve plungers slidably mounted in these sleeves, a directional control trace'r because the resultant movement of the cutter with respect to the Work depends upon the radial direction in which the tracer is deflected with respect to the vertical axis of the tracer head. It will be noted that each of the sleeves shown in Figure 4 is provided with three annular grooves, and radial holes in these grooves form ports. Theinside ports 2|1,'2|8, 2|9 and 220 in the respective sleeves are pressure ports and as shown in Figure 9 are all connected to the feed pump delivery channel |64. The middle ports 22|, 222, 223 and 224 are connected by separate channels 225, 226, 221 and 228 to ports 229, 230, 23| and 232 of the selector valve mechanism.

The outside ports 233, 234, 235 and 236 are connected to a common return channel 231. It will now be s een that each valve sleeve is provided with a pressure port, an intermediate motor port, and an exhaust port.

Each sleeve is provided with a xalve plunger which, as shown in Figure 3, has an annular groove 238 of such width that when in a central position the pressure port and exhaust port are closed so that upon movement of the plunger, either the pressure port or the exhaust port will be connected to the motor port. Thus, each valve is capable of causing one direction of movemeit, that is, by connecting pressure to a motor por When the selector valve mechanism is in the position shown in Figure 9, thev ports 229, 230, 23| and` 232 are disconnected from the table and cross slide cylinders 2l and 24, but in order to prevent damage to the tracer in case same is inadvertently deflected during manual or' power actuation of either slide, these various ports are connected to a pilot valve mechanism which will, when actuated, Acause automatic shifting of the selector valve mechanism into a tracer controlled position.

Therefore. when the selector valve mechanism' 1s in the position shown, each of the ports 229, 238, 23|. and 232 are connected to the pilot valve mechanism so as to cause actuation thereof when fluid pressure is admitted to any of channels 225, 226,221 or 228 by deflection of the tracer. In other words, the port 229 is connected through annular groove 238 to port 239 from which a channel 240 extends to port 24| of the pilot valve mechanism, indicated generally by the reference numeral 242.

The port 238 is connected by annular groove 243 to port 244 from which channel 245 extends to port 246 of the pilot valve mechanism. The ports 23| and 232 are connected by annular grooves 241 and 248 to ports.249 and 258 respectively from which extend channels 25| and 252 to ports 253 and 254 respectively of the pilot valve mechanism.

The pilot valve mechanism comprises two valve housings 255 and 256 having pressure ports 251 and 258 respectively, which are supplied with fluid through a branch 259 of the feed pump delivery ,channel |65. The valve housing 255 has 265 which is reciprocably mounted in a bore =i 266. This bore terminates at opposite ends in larger bores 261 and 268.

The plunger 265 has a length equal to the length of the bore 266 so that spring pressed washers 269 and 218 mounted in the largerbores 261 and 268 can hold the plunger 265 in a central position with respect to its bore. Bolts 213 and 214 are threaded in opposite 'ends of the plunger, and springs 215 are interposed between the bolt lheads and the washers to hold the latter against the shoulders formed by the smaller bore and simultaneously against the end of the plunger. The valve housing 256 is provided with a similar plunger mechanism.

It will now be evident that if pressure is admitted to port 253, for instance,'and the port 24| connected to exhaust, which would happen upon deflection of the tracer in the plane of valve sleeves 2|| and 2|3, the pressure-acting in chamber 268 would shift the plunger 265 upward as viewed in Figure 9, and thereby connect the pressure port 251 to port 268.

'I'he fluid would then ow through channel 264 to chamber 216 in the upper end of the valve housing containing plunger 62 forcing the same downward and, through link 64, forcing the plunger 63 upward. This would position the selector valve mechanism in a tracer control position, and disable the power and manual control mechanism.

When the selector valve mechanism is shifted to a tracer control position the port 23| is connected by annular groove 15 to port 18 whereby the port 223 of the tracer mechanism controls the I admission of fluid to port 14 of the table cylinder 2|; the port 229 is connected by groove 16 to port 69 whereby the port 22| of the tracer mechanism controls the admission of fluid to port 13 of table cylinder 2|; the port 232 is connected by annular groove 88 to port 83 whereby the tracer port 224 controls admission of fluid to port 81 of the cross slide cylinder 24; and the port 238 is connected by groove 98 to port 9| whereby the tracer port 222 controls admission of uid pressure to'port 86 of the cross slide cylinder 24. It will now be seen that both cylinders 2| and 24 are disconnected from their respective servo-control valves and are connected to the tracer control valves.

The valve housing 8| has a pressure port 211 which is supplied with fluid from channel |65 and when the selector valve is shifted to a tracer control position this port 'is connected to port 218. A channel 219 extends from this port to a series of interlocking devicesy associated with the respective .power transmissions, one device functioning to rotate the control shaft |33 to a neutral position and the other to effect disengagement of the half-nuts |0| from the servocontrol lead screw 99. y

The first device comprises a pair of cylinders 280 and 28| in which are mounted plungers 282 and 283. As shown in Figure 7 the shaft |33 has a double-ended lever 284 keyed thereto and positioned in front of a housing 285 and in which the cylinders 288 and 28| are formed so that the plungers 282 and 283 engage opposite ends of the lever.

When no pressure is in the cylinders the lever may be rotated freely but when pressure is admitted to the cylinders the pistons function to rotate the lever to a neutral position. A similar set of pistons and levers are .provided for the other transmission as shown in Figure 9 and connected in parallel to channel 219.

'I'he second device consists of a hydraulically actuated plunger 286 which is carried in the enlarged end |00 of the servo-valve sleeve 41 and when pressure is admitted thereto, it 'lifts the half nut |0| out of engagement with the screw.

As shown in Figure 6, the plunger 286 is connected by an interdrilled channel 281 to an annular groove 288 formed in the sleeve 41 which is in constant communication with a port 289 formed in the housing 4|. It will now be apparent that the shifting of the selector valve mechf anism places the tracer control mechanism in commanz.` of th.; operation of the table and cross slide, and neutralizes the power transmission as well as disabling same where-by rotation`of the hand wheel |06 will produce no movement of the servo-valve when the same is rendered ineffective.

Referring to Figure 3, the tracer arm 2 I5, which is pivotally supported in the tracer head, -carries an octagonal block 298, and the tracer valve plungers 29| are connected to opposed pairs of faces of this block by rods 292. These rods are threaded into the block and pass through central bores 293 in the respective plungers and consleeves 295. The sleeves are held against outward movement by lock nuts 297. A spring 298 is mounted between the end of the sleeve and a shoulder 29S to thereby exert a continuous urge in an outward direction. These centralizing devices are arranged in opposing pairs and by adjustment of the various lock nuts 291, the tracer may be centralized.

The tracer arm 2l5 is normally held against lifting by a spring 300 interposed between a fixed shoulder 30| and a shoulder 302 which is attached to the arm. The shoulder 302 is formed on a sleeve 3&33 which has a conical shaped end 3M. A feed rate adjusting sleeve 365 is threaded at Sli@ in the tracer head and provided with a bore 3W through which passes the cone 304. By vertical adjustment of the sleeve 35 the amount of lost motion between the cone and the bore 301 may be varied. This limits the amount that the operator can deflect the tracer and thereby determines the maximum feed rate that can 'be effected by the tracer valve.

A hydraulic interlock has been provided which acts as a safety precaution against the operator moving the head I6 downward and thereby moving the tracer into engagement with some obstruction which would cause damage thereto. In other words, if the head is moved downward and the end of the tracer engages an obstruction the tracer is movedaxially upward and thereby shifts a valveI plunger 3GB mounted in the valve block 2m, connecting pressure port 309 to port 3|!! which has a channel 3H connected thereto and leading to a cylinder 3l2. This cylinder contains a plunger 3l3 which will rock the half nut 3| 4 out of'engagement with the servo-screw 3I5.

The operator controls the operation of themachine by first positioning the lever 66 in accordance with the method of milling to be performed. If plane milling is selected the selector valve mechanism will be positioned by the lever to connect the servo-valves 4| and 5| for control of their respective pistons. The control lever |42 is then moved to select the direction and rate of relative movement between the cutter and work. If the rate of movement is rapid traverse, the operator must hold the lever M2 in its raplf traverse position, otherwise it will automaticalli return to a feed position. Trip dogs SIB may be applied to the moving slide for automatically tripping the lever I 42 from a feed position to a stop position.

Since no means are provided for automatically reversing the direction of movement, the operator must move the lever to obtain a. new direction of movement.

When the control lever M2 is in a neutral position, the manual control is automatically rendered available for slide adjustment and is usually utilized when setting up the machine.

For profile milling the lever $6 is thrown to its other position whereby the selector valve mechanism is hydraulically connected for control by the tracer head.

The operator places a work piece and a pattern on the work table the same distance apart as the cutter and tracer and then deects the tracer manually into contact with the pattern to cause a corresponding direction of movement of the cutter. This direction of movement will be such as to cause undeilection of the tracer and it is necessary for the operator to continually maintain the tracer deflected and in contact with the pattern in arder to maintain the cutting action and cause the cutting'to'ol to follow a path corresponding to the outline of the pattern. It will be noted that the tracer is the only element that can cause movement of the tool in this method of milling and that the direction of movement isv 'I'here has thus been provided an improved milling machine which may be safely utilized for either one of two methods of milling and which may be easily and quickly converted from a plane milling machine to a profile milling machine..

We claim:

1. In a milling machine having a cutter support and a work support, the combination of a power transmission for effecting relative movement between the supports including a rate determinator having a feed position and a rapid traverse position, a direction determinator having three diierent positions, a cam shaft having separate cams thereon and operatively connected for controlling each of said determinators, a control lever for rotating said shaft, detent means for holding the lever in any one of the three positions corresponding to the three positions of the direction determinator, said lever being movable against the resistance of said detent means to other positions to cause actuation of ,said rate determinator, said detent means being effective upon release of the lever to return it to a feed Position.

2. In a milling machine having a cutter support and a work support, the combination of transmission means including a. final shaft for actuating one of said supports, a manual actuator for said shaft, a clutch for connecting the actuator to the shaft. lfluid pressure operable means continuously urging the clutch to an engaged position, a power transmission for said final shaft, control means therefor including a cam shaft'having means thereon for causing said power transmission to produce different effects on said final shaft, said cam shaft having a neutral position wherein said power transmission is disconnected from the final shaft, and means operable when said cam shaft is rotated to a power operating position for disengaging said firstnamed clutch.

3. In a milling machine having a cutter support and a work support. the combinationof transmission means including a. fluid actuable element connected to the support, a source of fluid pressure, a control valve for connecting said fluid pressure to said element. manual operable means for shifting said valve, a clutch interposed between said manual actuable means and said control valve means. a piston responsive to fluid pressure for normally holding said clutch in an engaged position, and means for disconnecting said clutch upon failure of said fluid pressure.

4. In a milling machine having relatively translatable supports, the combination with 'hydraulic means for driving one of said supports including a servo-control valve and a first pump for supplying fluid pressure to said valve, of a power transmission for actuating said valve, cam operated means effective on said transmission for determining the rate and direction oi' movement Of said servo-valve, a control shaft for said cam means, a manual actuator for said servo-control t valve and normally connected thereto, means op.- erable by said control shaft for disabling said manual control means during power actuation of the servo-control valve, a second pump for supplying additional fluid pressure during rapid traverse actuation of said servo-control valve, and cam operated power means controlled by said shaft for connecting said second pump to the servo-valve for volumetrically increasing the delivery thereto during rapid traverse movement of the support.

5. In a milling machine having a pair of transversely movable slides, one of which is adapted to carry a .cutter and the other to supfor effecting relative movement between the tool support and the work support universally in a plane at rightangles to the axis of the tracer,

a source of fluid pressure, servo-valve means for port, a work support, and a tracer carried by port a work piece, the combination of fluid operable pistons moving the respective supports, separate control valve. means for each of said pistons, a common pump for supplying fluid to said control valve means, seaprate power actuable means for operating the respective valve means at different rates to produce feeding movements or a rapid traverse movement of the connected supports, a rapid traverse pump and-means for combining the delivery of said rapid traverse pump with said feed pump upon rapid traverse actuation of said control valve.

6. In a milling machine having a pair of supports, one of which carries a cutter and the other adapted to support a work piece, the combination with separate fluid operable pistons-'for moving the respective supports, of control means including a first valve mechanism for determining the admission of fluid pressure to said pistons, a second valve mechanism, a tracer for controlling one of said valve mechanisms, power-operable means for controlling the other valve mechanism, and a selector valve for determining which of said valve mechanisms shall control the relative movement between said supports.

7. In a profiling machine having a tool support, va work supporting table, and a tracermounted on said tool support for engaging a pattern carried by the table, the combination of fluid voperable means for feeding the table, a

- source of pressure therefor, valve means for connecting saidv source of pressure to the fluid operable means, an actuator for said valve means whereby said table may be power positioned with respect to the tracer, and means responsive to inadvertent deflection of the tracer during said lpositioning-to disconnect the actuator Vfrom said ValVe means.

8. In a profiling machine having a tool supany of said channels for connecting said motor.

movement of the table, and additional means res e tracer being perpendicular to the plane of the table, the combination of fluid operable means the tool support, the normal axis of said tracer being perpendicular to the plane of thel table, the combination of fluid operable means for effecting relative movement between the tool support and the Work support universally in a plane alt right angles to the axis of the tracer, a source of fluid pressure, servo-valve means *for connecting said source of fluid pressure for actuation of said fluid operable means, power actuating means for said servo-Valves, means responsive to lateral deflection of the tracer during power'actuation of said valve means for effecting disconnection of said power means causing cessation of the relative movement, and automatic means for repositioning the supports until the deflection of the tracer has been removed.

11. In a profiling machine having a tool support and a work support, the combination with a tracer mounted on said tool support, of fluid operable motors for actuating each support, a source of fluid pressure, valve means for con- .necting said fluid pressure to said motors, a

tracer head for supporting said tracer and including valve means having a plurality of motor channels extending therefrom, means connecting the source of fluid pressure to said head whereby upon deflection of the tracer said source of pressure will be connected to said motor channels, and means responsive to pressure in channels exclusively to the motors for control thereof. A

l2. A milling machine having a work supporting table, a tool spindle, means to support the spindle for two-directional movement with respect to the table, a tracer supported for bodily movement' with the spindle, different. control means connectible for moving the table and for effecting the two directions of movement of the spindle and tracer, and means responsive to deflection of the tracer during actuation of any one of said controls for automatically disabling said control. v

13. In a profiling machine having a pair of slides movable in paths normal to each other, the combination of a cutter spindle and a tracer carried by one of said slides, a hydraulic motor for' actuating each slide, a servo-control valve yfor each motor, additional valve means controlled by the tracer, a selector valve, hydraulic channels conneoting the servo-valves and the tracer controlled valves to said selector valve, said selector valve being alternatively positionable to connect either Aset of channels to the hydraulic motors, fluid operable means for shifting said selector valve to a tracer controlled position, and means responsive to pressure in any of the channels leading from the tracer valve to cause operation of said fluid operable means.

14. In; a profiling machine having a pair of relatively movable supports, a cutter spindle and a tracer carried by one of said supports, the

combination of separate fluid operable motors for actuating each support, a servo-control valve and a tracer control valve alternatively connectible for governing operation of said motors, a selector valve for eiecting said alternative connections, power operable means for actuating said servo-valves including a control shaft having a plurality oi' active positions and a neutral position, means responsive to deflection of the tracer when the control shaft is in any one of its active positions, causing movement of one of said supports, to automatically cause shifting of the selector valve to its tracer controlled position and simultaneously to position said control shaft in its neutral position.

15. In a proling machine having a table and a tool slide, the combination of a tracer mechanism carried by one of said slides, fluid operable motors of the piston and cylinder type connected to the table and slide, said cylinders being arranged in planes normal to one another, said tracer mechanism including a tracer head including a plurality of radially arranged valves, there being a separate valve for controlling the iloW of fluid to and from one end of the cylinders, said valves lying in planes parallel rto the cylinders which they control, a tracer arm pivotally supported in a central relation with respect to said valves and connected thereto, a series of equally spaced compression springs radially arranged intermediate said valves and connected to said tracer arm for normally maintaining the by one of said slides and a pattern carried by.

the other, the combination of uid operable motors for moving each slide, servo-valve mechanisms for each motor, a selector valve positionable for connecting said servo-valves to the respective motors, tracer controlled valves having channels leading to said selector valve, means normally centralizing said tracer and holding said tracer controlled valves in a closed position,

uid operable means for shifting said selector valve to connect said channels to said motors, a pilot valve mechanism connectible to said Vchannels by the selector valve mechanism including a plurality of resiliently centralized plungers, and means responsive to pressure in any of said channels for shifting one of said plungers to connect a source of pressure to said fluid operable means and cause shifting of said selector valve to a tracer controlled position, whereby said channels are connected for the control of said motors.

ERWIN G. ROEHM.

HANS FRITSCHI. 

